Internal combustion engine



1937- I N. w. KINNEY 2,091,120

INTERNAL COMBUST ION ENGINE Filed April 25, 1955 4 Sheets-Sheet l Aug. 24 1937. N. w. KINNEY 2,091,120

INTERNAL COMBUSTION ENGINE Filed April 25, 1955 4 Sheets-Sheet 2 4 Sheets-Sheet 3 Aug. 24, 1937. N. w. KlNNEY INTERNAL COMBUSTION ENGINE Filed April 25, 1935 Aug. 24, 1937. N. w. KINNEY 2,091,120

INTERNAL COMBUSTION ENGINE Filed April 25, 1955 4 Sheets-Sheet 4 WK In) HRQJ. Q? S m NW %N 8am WW rm .v mmfl & Kw hum N\ lllllllfllw w lllllmai R 0 N u mm. v Mm 6M 9w 4 v .v 7 MN, x X a ir RN MN Q \h% Patented Aug. 24, 1937 UNi'i' E STATES INTERNAL COMBUSTION ENGINE Norton W. Kinney, Groveland, Mass.

Application April 25,

4 Claims.

This invention relates to rotary, or turbine, internal combustion engines and it has for its object to improve the construction and operation of engines of this class.

To these ends I have provided an improved internal combustion engine having the peculiar features of construction and operation set forth in the following description, the several novel features of the invention being separately pointed out and defined in the claims at the close thereof.

In the accompanying drawings:

Figure 1 is a central longitudinal sectional View of an internal combustion engine constructed in accordance with this invention, the plane of the section being on line l! of Fig. 2. v

Figure 2 is a section on line 22 of Fig. 1.

Figure 2a is a fragmentary sectional view of one of the compression eccentrics hereinafter referred to.

Figure 3 is a sectional detail hereinafter referred to. Figure 4 is a section on line 4-4 of Fig. 1." Figure 5 is a section on line 5-5 of Fig. 2.

Figure 6 is a section on line 66 of Fig. 2.

Figure '7 is a diagrammatic end view of the four eccentric portions of the rotor hereinafter referred to and illustrating their angular relationship.

The illustrated embodiment of my invention comprises an interiorly cylindrical casing [8 which may be constructed, as shown, to provide a water jacket H and which may be provided at its opposite ends with apertured heads l2, l2 having base portions i2a adapted to be secured in position upon a suitable support.

Within the casing i is a tubular rotor member which is indicated generally at 93 in Fig. 1 of the drawings and this rotor member is constructed with hubs M fixed in position upon a shaft i journaled in bearings provided in the heads l2. This shaft l5 carries a flywheel 29. The hubs M are connected with the outer tubular portion of the rotor by radial arms :6 which serve as fan blades to cause a flow of air through the tubular rotor member l3, said air entering the apertures i I provided through the head I 2 at one end of the casing and being discharged through the apertures l8 provided through the head l2 at the opposite end of the casing. Thus while the engine is in operation the rotor 13 is cooled interiorlyby a draft of air flowing therethrough and exteriorly by the water jacket l l of the casing.

The rotor i3 is constructed so that it is composed of a plurality of sections the peripheries of some of which are eccentric with respect to the 1935, Serial No. 18,180

axis of the rotor while the'peripheries of other sections are concentric with respect to the axis of said rotor. As herein shown there are two pairs of eccentric sections 19 and 20 and l9a. and 20a and five cylindrical concentric sections 2|, 22, 23, 24 and 25, the concentric cylindrical section '22 fitting the cylindrical interior of the casing and being disposed between the pair of eccentric sections l9 and 20 and the cylindrical concentric section 24 also fitting the cylindrical interior of thecasing and being disposed between the sections I94; and 20a.

The two cylindrical sections 2| and 22 provide between them a combustion and expansion chamber within which is disposed the motor eccentric 20; the two cylindrical sections 22 and 23 provide between them a compression chamber 25 which is occupied bythe gas compressing eccentric l9; the'two cylindrical sections 23 and 24 provide between them another compression chamber 2'! within which is disposed the gas compressing eccentric lfla, while the two cylindrical sections 24 and 25 provide between them a combustion and expansion chamber 28 within which the motor eccentric 20a is disposed.

Figure '7 illustrates the angular relationship existing between the sections l9, Illa, 20 and 20a.

Referring to this figure of the drawings, the radial line W bisects the portion of greatest radius of section 20; the radial line Y bisects the portion of greatest radius of the section 2011; the radial line X indicates the portion of greatest radius of the section l9, and the radial line Z indicates the portion of greatest radius of the section l9a.

As shown in Fig. 6 the casing in is constructed with two radial slots and 30a communicating at their innerends, respectively, with compression chamber26 and compression chamber 27!. Within the slot 30 is slidably mounted a gate or partition member 3| whose inner end is equipped with a rocker shoe 32 bearing continuously against the periphery of eccentric l9.

Within the slot 30a'is slidably mounted a similar gate or partition member 33 whose inner end is likewise equipped with a rocker shoe 34 hearing continuously against the periphery of the eccentric l9a.

The peripheries of the eccentrics. l9 and [9a are truly circular and said eccentrics are relatively disposed angularly one hundred and eighty degrees apart so that the gates 3| and 33 must move correspondingly but in opposite directions as the eccentrics are rotated in order to maintain continuous contact with said eccentrics.

Upon its exterior the casing I is made with a pair of parallel spaced apart lugs 34, Figs. 2 and 6, supporting the opposite ends of a pivot pintle 35 on which is swivelly mounted a fulcrum block 36 occupying a position within a slot 31 formed in a walking-beam lever 38. At its opposite ends the lever carries rolls 39 and 40, the former abutting the outer end of gate partition 3| and the latter abutting the outer end of gate partition 33.-

A stiff spring 4! occupies a position within slot 31 and between block 36 and the inner end of said slot. This spring is installed under initial compression and serves to yieldingly urge the lever 38 toward the gate partitions 3| and 33 so that the rolls 39 and 40 are maintained continuously in contact with said gate partitions. Thus as each gate partition is shoved outwardly by its eccentric it acts through the walking-beam lever 38 to shove the other gate partition inwardly as the eccentric of the latter recedes, the spring 4| maintaining both gate partitions always in contact with their eccentrics.

The compression chambers 26 and 21 are provided, respectively, with gas inlet ports 42 and 43 each disposed at the rear of its gate partition and in close proximity thereto. Therefore, while either eccentric is rotating in the direction indicated by the arrow in Figs. 2 and 4 it co-operates with its gate partition to draw gas into the casing at one side of said gate partition while at the same time, it compresses a charge of gas at the opposite side of said gate partition which was drawn into the casing during the preceding revolution of the eccentric. i

The concentric cylindrical section 22 of the rotor serves the double function of a partition normally separating the compression chamber 26 from the combustion chamber 25 and also as a valve controlling communication between said two chambers, and the concentric cylindrical section 24 is likewise co-operatively associated with the compression chamber 21 and combustion chamber 28. The concentric cylindrical section 23 of the rotor serves only as a partition separating chamber 26 from chamber 21. The concentric cylindrical end sections 2| and 25 serve only as side walls for the combustion chambers.

The peripheries of the eccentrics 20 and 20a are not truly circular and these two eccentrics are relatively disposed angularly 180 degrees apart and each is disposed relatively to its compression eccentric i9 01 lea 90 degrees in advance of the same, as illustrated in Fig. 2 of the drawings. As shown in Figs. 2 and 2a, a portion of the periphery of the eccentric 26 measuring circumferentially about 60 degrees is concentric with the axis of the shaft l and of approximately the same radius as the interior of the'casing ID. The remaining portion of the periphery of the eccentric 26 measuring circumferentially about 300 degrees'is a circular are that is concentric with a center that is oiT-set with respect to. theaxis of the shaft 15. The eccentric 20a is similarly constructed but, as pointed out above, is disposed 180 degrees removed from the eccentric 26. Likewise, it will be clear that the two compression eccentrics I9 and [9a are positioned relatively 180 degrees apart and each 90 degrees to the rear ofits eccentric 26 or 20a. 4

As will be clear from Figs. 2 and 5; the casing I0 is constructed with two radial slots 43 and 43a communicating at their inner ends, respectively, with expansion chamber 25 and expansion chain ber 28. Within the slot 43 is slidably mounted a gate or partition member 44 whose inner end is equipped with a rocker shoe 45 bearing continu ously against the periphery of eccentric 20. Within the slot 43a is slidably mounted a similar gate or partition member 46 whose inner end is likewise equipped with a rocker shoe 4'! bearing continuously against the periphery of the eccentric 20d.

Since the expansion eccentrics 20 and 200. are relatively disposed angularly 180 degrees apart while the two gate partitions 44 and 46 are alined longitudinally relatively to the shaft l5, said two gate partitions must move correspondingly and in unison but in opposite directions as the expansion eccentrics are rotated and when the engine is in operation such is the case.

Upon its exterior the casing I6 is made with a pair of parallel spaced apart lugs 48, Figs. 2 and 5, supporting the opposite ends of a pivot pintle 49 on which is swivelly mounted a fulcrum block 50 occupying a position within a slot 5| formed in a walking-beam lever 52. At its opposite ends the lever 52 carries rolls 53 and 54, the former abutting the outer end of gate partition 44 and the latter abutting the outer end of gate partition 46.

A stiff spring 55 occupies a position within the slot 5| between block 50 and the inner end of said slot and this spring is installed under initial compression and serves to yieldingly urge the lever 52 toward the gate partitions 44 and 46 so that the rolls 53 and 54 are maintained continuously in contact with said gate partitions. Thus, as each gate partition is shoved outwardly by its eccentric 20 or 20a it acts through the walkingbeam lever 52 to shove the other gate partition inwardly as the eccentric of the latter recedes, the spring 55 maintaining both gate partitions always in contact with their eccentrics.

The expansion chambers 25 and 28 are provided, respectively, with exhaust ports 55and 51, Figs. 2 and 1, each disposed in front of its gate partition and in close proximity thereto. Therefore, while either eccentric 20 or 20a is rotating in the direction indicated by the arrow in Fig. 2, it cooperates with its gate partition to expell the spent gases of the preceding revolution thereof through the exhaust port of its chamber during which time a fresh charge of gas is supplied to the expansion chamber, or rather to a pocket or extension of said expansion chamber forming part of the latter, said pocket or extension being disposed in close proximity to, and at the rear of, its gate partition 44 or 46. In Fig. 2 the pocket or extension of expansion chamber 25 is shown at 58 while the corresponding pocket or extension of chamber 28 is indicated in Fig. 1 by dotted lines at 59.

The casing I0 is made with an approximately radial port 60 communicating at its inner end with the pocket or extension 58 of chamber 25 and into this port is screwed a spark plug 6| as shown in Fig. 2.

The extension 59 of chamber 28 is likewise provided with a spark plug 6|.

Upon its interior the casing I0 is formed with a longitudinal groove or channel 62 communicating at its one end with the pocket or extension 58 of chamber 25, said channel or groove 62 extending longitudinally part way across the periphery of the circular section 22 of the rotor. This circular section 22 of the rotor is made upon its periphery with a longitudinal channel or groove 63 which communicates at its one end with the chamber 26 of the compression eccentric l9. It will thus be clear thatthe two channels or grooves 62 and 63 bear overlapping relationship relative- 1y so that once during each revolution of the rotor |3 the channel or groove 83 registers with the channel or groove 62 formed in the casing. The casing I0 is also formed upon its interior with another longitudinal channel or groove 62a that is disposed opposite the periphery of the partition section 24 of the rotor and communicates at its one end with the pocket or extension 59 of expansion chamber 28. Also, the partition section 24 of the rotor is made upon its periphery with a longitudinal channel or groove 63a. which communicates at its one end with the compression chamber 2'! and which bears overlapping relationship with the channel or groove 62a. so that once during each revolution of rotor I3 the channel or groove 83a registers with the channel or groove 6201..

As the portion of compression eccentric I9 that is of greatest radius approaches its gate partition 3| (just back of its position as illustrated by dotted lines in Fig. 2), the channel 63 comes into register with the channel 62 with the result that the compressed gas within chamber 26 between said portion of greatest radius and the gate partition 3| discharges from chamber 26 through channels 53 and 62 into the pocket or extension 58 of chamber 25. This delivery of compressed gas into the pocket or extension 58 occurs, or is initiated, just before the portion of greatest radius of eccentric 20 completely closes the pocket or extension 58 with the result that the first eifect of the entering fresh gas is to scavenge said pocket or extension and immediate-- ly thereafter communication between pocket or extension 58 and chamber 25 is shut oif by said portion of greatest radius.

Immediately after the channel 53 has passed the channel 62 the spark plug BI is operated to ignite the charge within the pocket or extension 58. Fig. 2 shows the relation of the parts at the moment that the spark plug 5| is thus operated.

When the charge within the pocket or extension 58 is thus ignited it is confined within a space defined by the casing I0, gate partition 44 and the portion of eccentric 2! that is of greatest radius with the result that said eccentric is forced to turn in the direction of the arrow, and since the exhaust of this ignited charge does not start until said portion of greatest radius has passed the exhaust port 56, it will be clear that during the greater portion of the revolution of eccentric 20 the gas is acting expansively upon the said eccentric.

The eccentrics [9a and 20a. together with the partition section 24 jointly co-operate in a similar fashion but the power stroke of eccentric 20a, occurs 180 degrees after the power stroke of eccentric 20. It will thus be clear that there are two power strokes during each revolution of rotor l3 timed 180 degrees apart.

As will be clear, each gate partition of each pair is positively moved outwardly by its eccentric during one-half of the revolution of the l rotor and during the other half of the revolution of rotor |3 the other eccentric of that pair acts through the walking-beam associated with said pair to yieldingly force said gate partition. inwardly and maintain it in contact with its eccentric.

Figure 3 is a sectional detail illustrating the construction of the gate partition 3|. As shown in this figure, the inner end of the gate partition 3| is formed with a socket 64 within which is mountr ed to rock a rocker shoe 32, said shoe being held within said socket by means of the head of a screw 65 whose shank extends through an arcuate slot '66 formed through the rocker shoe 32. This screw 65 and the slot 66 may be disposed midway between the opposite ends of the rocker shoe.

The other rocker shoes 34, 45 and 41 are constructed and applied to their gate partitions in a similar manner.

Each concentric partition section 22, 23 and 24 of the rotor is formed upon its periphery with two circular grooves in each of which is mounted a packing ring 6? similar to a piston ring in that it may be split and press yieldingly against the interior of the casing. These packing rings serve to prevent leakage from one chamber to the next chamber or chambers. Similar packing rings 68 may be provided in grooves formed upon the peripheries of the end sections 25 of the rotor.

In practice I may, and preferably do, provide joint-closing packing devices for the gate partitions 3|, 33, 44 and 46'and in other places where desired.

At the moment that the channel 63 passes beyond the casing channel 62 a small body of gas will occupy the space between the portion of greatest radius of the compression eccentric I9, and gate 3|, Fig. 2, and in order to evacuate this body of gas as said portion. of greatest radius approaches the gate partition 3| I form the periphery of the compression eccentric l9 with an arcuate by-pass groove 69 which is shown near the top of Fig. 1 and by dotted lines at the top of piston H in Fig. 2, said groove occupying a position opposite the gate partition 3| as said portion of greatest radius moves up to the latter. Therefore, the trapped body of gas referred to is transferred through the by-pass 69 under the gatepartition 3| and into the space upon the intake side of gate partition 3|.

The compression eccentric |9a is likewise provided with a similar by-pass groove 10, Fig. 1,

for the same purpose.

The channels 53 and 63a extend under the adjacent packing rings 6'! so that the latter does not interfere with the fiow of gas through said channels.

In order to prevent leakage of gas under pressure circumferentially around the partition section 22 either from the channel 62 or from the channel 53 Fig. 1, the said partition section 22 is made upon its periphery with transverse grooves Ila in each of which is mounted a packing strip 1| each of which is yieldingly urged outwardly by a spring 12. The partition section 24 is similarly constructed upon its periphery with packing strips H to prevent the passage or leakage of gas under pressure circumferentially from either the channel 62a or the channel 63a.

Also, each expansion eccentric 2|] and 20a is, as shown in Fig. 2, formed upon the periphery of its portion of greatest radius with a transverse groove or channel 14, Fig. 2a within which is mounted a metal packing strip 13 which is yieldingly held against the interior of the casing at all times by a spring 14 as shown in Fig. 2a. This packing strip I3 occupies a position in front of the ignited and expanding charge during the power stroke of the said eccentric.

The two eccentric sections I9 and |9a are exteriorly cylindrical and their radii of greatest length are disposed 180 degrees apart relatively. The two eccentric sections 20 and 2011 have their portions of greatest radius angularly disposed 180 degrees apart and the portion of greatest radius of each is angularly disposed 90 degrees in advance of its complemental eccentric section I9 or [9a. Owing to the cylindrical form of the eccentrics l9 and l9a each contacts with the Wall of its chamber 26 or 21 approximately along a line only. On the other hand, each of the eccentrics and 20a is made with the portion of its periphery between the radial lines a and b, Fig. 2a, concentric with the axis of the shaft l5 so that each has extended surface contact with the circular wall of its chamber or 28. In the illustrated embodiment of the invention a radial line bisecting the angle ab, Fig. 2a, of each section 20 and 20a is disposed at right angles with respect to the line of greatest radius of its complemental section H! or l9a.

What I claim is:

1. A rotary internal combustion engine having, in combination, a casing constructed with in- 20 let and exhaust ports and having a cylindrical interior from end to end thereof; a rotor mounted within said casing comprising three sections including an intermediate partition section having a cylindrical periphery fitting the interior of said casing and dividing said interior so as to provide a compression chamber at one side thereof and an expansion chamber at the opposite side thereof, said periphery being formed with a longitudinal groove extending only part way across the same and communicating at its one end only with said compression chamber, an eccentric gas compressing section fitting within said compression chamber, and an eccentric motor section fitting within said expansion chamber, the interior of said casing being made with a longitudinal groove disposed opposite said partition section and communicating at its one end only with said expansion chamber and disposed relatively to the path of said first mentioned groove so that once during each revolution of said rotor the two grooves register and overlap axially thereby to permit the passage of compressed gas from the compression chamber through said grooves into said expansion chamher; a radially movable abutment gate slidably supported by said casing and continuously engaging the periphery of said gas compressing section; a radially movable abutment gate slidably supported by said casing and continuously engaging the periphery of said motor section, and

means for yieldingly holding said gates each in contact with its section.

2. A rotary internal combustion engine constructed in accordance with claim 1 wherein said gas-compressing section is made upon its periphery with a circumferential by-pass through which the compressed gas occupying the space within the compression chamber between said gas compressing section and the gate of said section, after the groove of said intermediate partition section moves out of register with the groove of the casing, is transferred to the intake side of said gas-compressing section.

3. A rotary internal combustion engine constructed in accordance with claim 1 and wherein said gas-compressing section is made upon its periphery with a circumferential by-pass, through which the compressed gas remaining within the space within the compression chamber between said gas compressing section and the gate of said section, is transferred to the intake side of said gas-compressing section immediately after the groove of said intermediate partition section moves out of register with the groove of the casing. i

4; A rotary internal combustion engine having, in combination, a casing constructed with inlet and exhaust ports; a rotor mounted within said casing comprising three sections including an intermediate partition section having a cylindrical periphery fitting the interior of said casing and dividing said interiorso as to provide a compression chamber at one side thereof and an expansion chamber at the opposite side thereof, an eccentric gas-compressing section fitting within said compression chamber and an eccentric motor section fitting within said expansion chamber; a movable gate mounted on said casing and continuously engagingthe periphcry of said gas-compressing section; a movable gate mounted on said casing and continuously engaging the periphery of said motor section, and means for yieldingly holding said gates each in contact with its. section, the intermediate partition section of said rotor being provided upon its periphery with a groove which axially overlaps and registers with a groove upon the interior of said casing once during each revolution of said rotor thereby to permit the passage of compressed gas from the space in advance of said gas-compressing section into the space behind the portion of greatest radius of said motor section. V

NORTON W. KINNEY. 

